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JP4254217B2 - Ejector cycle - Google Patents

Ejector cycle Download PDF

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Publication number
JP4254217B2
JP4254217B2 JP2002345341A JP2002345341A JP4254217B2 JP 4254217 B2 JP4254217 B2 JP 4254217B2 JP 2002345341 A JP2002345341 A JP 2002345341A JP 2002345341 A JP2002345341 A JP 2002345341A JP 4254217 B2 JP4254217 B2 JP 4254217B2
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JP
Japan
Prior art keywords
refrigerant
compressor
pressure
heat exchanger
gas
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
JP2002345341A
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Japanese (ja)
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JP2004177027A (en
Inventor
素弘 山口
宏己 太田
幸正 佐藤
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Denso Corp
Original Assignee
Denso Corp
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Priority to JP2002345341A priority Critical patent/JP4254217B2/en
Priority to US10/721,656 priority patent/US6868679B2/en
Priority to DE10355315A priority patent/DE10355315A1/en
Publication of JP2004177027A publication Critical patent/JP2004177027A/en
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Publication of JP4254217B2 publication Critical patent/JP4254217B2/en
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
    • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
    • B60H1/00899—Controlling the flow of liquid in a heat pump system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • F04F5/02—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being liquid
    • F04F5/04—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being liquid displacing elastic fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H2001/3286—Constructional features
    • B60H2001/3298—Ejector-type refrigerant circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0012—Ejectors with the cooled primary flow at high pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0013—Ejector control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0014—Ejectors with a high pressure hot primary flow from a compressor discharge
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0403—Refrigeration circuit bypassing means for the condenser
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0407—Refrigeration circuit bypassing means for the ejector
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21163—Temperatures of a condenser of the refrigerant at the outlet of the condenser
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Fluid Mechanics (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Description

【０００１】
【発明の属する技術分野】
本発明は、エジェクタサイクルに関するもので、車両用空調装置に適用して有効である。
【０００２】
【従来の技術】
エジェクタサイクルとは、エジェクタにて冷媒を減圧膨張させて蒸発器にて蒸発した気相冷媒を吸引するとともに、膨張エネルギーを圧力エネルギーに変換して圧縮機の吸入圧を上昇させる蒸気圧縮式冷凍機である（例えば、特許文献１参照）。
【０００３】
一方、他の方式の蒸気圧縮式冷凍機としては、オリフィスやキャピラリーチューブ等の固定絞り、又は温度式膨脹弁等の可変絞りにて高圧冷媒を減圧して蒸発器に供給する膨脹弁サイクルがある（例えば、特許文献２参照）。
【０００４】
【特許文献１】
特開平５−１４９６５２号公報
【０００５】
【特許文献２】
米国特許６１７８７６１号明細書
【０００６】
【発明が解決しようとする課題】
ところで、膨張弁サイクルでは、冷媒が圧縮機→放熱器→膨張弁→蒸発器→圧縮機の順に循環する１つの冷媒流れとなるのに対して、エジェクタサイクルでは、圧縮機→放熱器→エジェクタ→気液分離器→圧縮機の順に循環する冷媒流れと、気液分離器→蒸発器→エジェクタ→気液分離器の順に循環する冷媒流れとが存在する。
【０００７】
このため、特許文献２に記載された発明と同様な手法にて、圧縮機から吐出した高圧・高温冷媒（ホットガス）を室内熱交換器に導入して暖房運転を行うことはできない。
【０００８】
本発明は、上記点に鑑み、第１には、従来と異なる新規なエジェクタサイクルを提供し、第２には、エジェクタサイクルにてホットガス運転モードを実現することを目的とする。
【０００９】
【課題を解決するための手段】
本発明は、上記目的を達成するために、請求項１に記載の発明では、低圧側の冷媒を蒸発させて低温側から吸熱し、高温側に放熱するエジェクタサイクルであって、冷媒を吸入圧縮する圧縮機（１０）と、室外空気と冷媒とを熱交換する室外熱交換器（２０）と、室内に吹き出す空気と冷媒とを熱交換する室内熱交換器（３０）と、高圧冷媒を減圧膨張させるノズル（４１）を有し、ノズル（４１）から噴射する高い速度の冷媒流により低圧側で蒸発した気相冷媒を吸引するとともに、膨張エネルギーを圧力エネルギーに変換して圧縮機（１０）の吸入圧を上昇させるエジェクタ（４０）と、エジェクタ（４０）から流出した冷媒を気相冷媒と液相冷媒とに分離し、気相冷媒を圧縮機（１０）に供給し、液相冷媒を低圧側に供給する気液分離器（５０）と、圧縮機（１０）から吐出した冷媒を減圧させながらエジェクタ（４０）を迂回させて室内熱交換器（３０）に導くバイパス手段と、圧縮機（１０）から吐出する冷媒を室外熱交換器（２０）に供給するクーラモードと圧縮機（１０）から吐出する冷媒をバイパス手段に供給するホットガスモードとを切り替える第１切替手段（６２）と、クーラモード時には、室内熱交換器（３０）から流出した冷媒をエジェクタ（４０）の低圧冷媒吸引口に導き、ホットガスモード時には、室内熱交換器（３０）から流出した冷媒をエジェクタ（４０）を迂回させて、気液分離器（５０）に導く第２切替手段（６３）とを備えることを特徴とする。
【００１０】
これにより、エジェクタサイクルにてホットガス運転モードを実現することができる。
【００１１】
請求項２に記載の発明では、低圧側の冷媒を蒸発させて低温側から吸熱し、高温側に放熱するエジェクタサイクルであって、冷媒を吸入圧縮する圧縮機（１０）と、室外空気と冷媒とを熱交換する室外熱交換器（２０）と、室内に吹き出す空気と冷媒とを熱交換する室内熱交換器（３０）と、高圧冷媒を減圧膨張させるノズル（４１）を有し、ノズル（４１）から噴射する高い速度の冷媒流により低圧側で蒸発した気相冷媒を吸引するとともに、膨張エネルギーを圧力エネルギーに変換して圧縮機（１０）の吸入圧を上昇させるエジェクタ（４０）と、エジェクタ（４０）から流出した冷媒を気相冷媒と液相冷媒とに分離し、気相冷媒を圧縮機（１０）に供給し、液相冷媒を低圧側に供給する気液分離器（５０）と、圧縮機（１０）から吐出した冷媒を減圧させながらエジェクタ（４０）を迂回させて室内熱交換器（３０）に導くバイパス手段と、圧縮機（１０）から吐出する冷媒を室外熱交換器（２０）に供給するクーラモードと圧縮機（１０）から吐出する冷媒をバイパス手段に供給するホットガスモードとを切り替える切替手段（６２）とを備え、ホットガスモード時には、室内熱交換器（３０）を流出した冷媒をエジェクタ（４０）に流入させることを備えることを特徴とする。
【００１２】
これにより、エジェクタサイクルにてホットガス運転モードを実現することができる。
【００１３】
請求項３に記載の発明では、低圧側の冷媒を蒸発させて低温側から吸熱し、高温側に放熱するエジェクタサイクルであって、冷媒を吸入圧縮する圧縮機（１０）と、室外空気と冷媒とを熱交換する室外熱交換器（２０）と、室内に吹き出す空気と冷媒とを熱交換する室内熱交換器（３０）と、高圧冷媒を減圧膨張させるノズル（４１）を有し、ノズル（４１）から噴射する高い速度の冷媒流により低圧側で蒸発した気相冷媒を吸引するとともに、膨張エネルギーを圧力エネルギーに変換して圧縮機（１０）の吸入圧を上昇させるエジェクタ（４０）と、エジェクタ（４０）から流出した冷媒を気相冷媒と液相冷媒とに分離し、気相冷媒を圧縮機（１０）に供給し、液相冷媒を低圧側に供給する気液分離器（５０）と、圧縮機（１０）から吐出した冷媒を減圧させながらエジェクタ（４０）を迂回させて室内熱交換器（３０）に導くバイパス手段と、圧縮機（１０）から吐出する冷媒を室外熱交換器（２０）に供給するクーラモードと圧縮機（１０）から吐出する冷媒をバイパス手段に供給するホットガスモードとを切り替える切替手段（６２）とを備え、ホットガスモード時には、室内熱交換器（３０）を流出した冷媒を、エジェクタ（４０）の低圧冷媒吸引口（４４）及びノズル（４１）の冷媒入口（４５）に導くことを特徴とする。
【００１４】
これにより、エジェクタサイクルにてホットガス運転モードを実現することができる。
【００１５】
請求項４に記載の発明では、クーラモード時及びホットガスモード時のいずれの場合においても、室内熱交換器（３０）内を流れる冷媒は、室内熱交換器（３０）を通過する空気の流れに対して、空気流れ下流側から空気流れ上流側に向かうように流れることを特徴とする。
【００１６】
これにより、室内熱交換器（３０）では、冷媒と空気とが対向流又は直交対向流状態で熱交換されるので、クーラモード時及びホットガスモード時のいずれの場合においても室内熱交換器（３０）での熱交換効率を高く維持することができる。
【００１７】
請求項５に記載の発明では、低圧側の冷媒を蒸発させて低温側から吸熱し、高温側に放熱するエジェクタサイクルであって、冷媒を吸入圧縮する圧縮機（１０）と、室外空気と冷媒とを熱交換する室外熱交換器（２０）と、室内に吹き出す空気と冷媒とを熱交換する室内熱交換器（３０）と、高圧冷媒を減圧膨張させるノズル（４１）、及びノズル（４１）から噴射する冷媒の巻き込み作用により低圧側で蒸発した気相冷媒を吸引しながら吸引した気相冷媒とノズル（４１）から噴射する冷媒とを混合させながら速度エネルギーを圧力エネルギーに変換して冷媒の圧力を昇圧させる昇圧部（４２、４３）を有し、圧縮機（１０）の吸入圧を上昇させるエジェクタ（４０）と、エジェクタ（４０）から流出した冷媒を気相冷媒と液相冷媒とに分離し、気相冷媒を圧縮機（１０）に供給し、液相冷媒を低圧側に供給する気液分離器（５０）と、圧縮機（１０）から吐出する冷媒を室外熱交換器（２０）→ノズル（４１）→昇圧部（４２、４３）→気液分離器（５０）→圧縮機（１０）の順に循環させるクーラモードと圧縮機（１０）から吐出する冷媒を室外熱交換器（２０）を迂回させて、ノズル（４１）→室内熱交換器（３０）→気液分離器（５０）→圧縮機（１０）の順に循環させるホットガスモードとを切り替える切替手段（６２）とを備えることを特徴とする。
【００１８】
これにより、エジェクタサイクルにてホットガス運転モードを実現することができる。
【００１９】
請求項６に記載の発明では、低圧側の冷媒を蒸発させて低温側から吸熱し、高温側に放熱するエジェクタサイクルであって、冷媒を吸入圧縮する圧縮機（１０）と、室外空気と冷媒とを熱交換する室外熱交換器（２０）と、室内に吹き出す空気と冷媒とを熱交換する室内熱交換器（３０）と、高圧冷媒を減圧膨張させるノズル（４１）、ノズル（４１）から噴射する冷媒の巻き込み作用により低圧側で蒸発した気相冷媒を吸引しながら吸引した気相冷媒とノズル（４１）から噴射する冷媒とを混合させながら速度エネルギーを圧力エネルギーに変換して冷媒の圧力を昇圧させる昇圧部（４２、４３）、及びノズル（４１）を収納するとともに昇圧部（４２、４３）の一部を構成するハウジング部（４８）を有し、圧縮機（１０）の吸入圧を上昇させるエジェクタ（４０）と、エジェクタ（４０）から流出した冷媒を気相冷媒と液相冷媒とに分離し、気相冷媒を圧縮機（１０）に供給し、液相冷媒を低圧側に供給する気液分離器（５０）と、圧縮機（１０）から吐出する冷媒を室外熱交換器（２０）→ノズル（４１）→昇圧部（４２、４３）→気液分離器（５０）→圧縮機（１０）の順に循環させるクーラモードと圧縮機（１０）から吐出する冷媒を室外熱交換器（２０）を迂回させてノズル（４１）の外壁部とハウジング部（４８）の内壁部との隙間に導き、室内熱交換器（３０）→気液分離器（５０）→圧縮機（１０）の順に循環させるホットガスモードとを切り替える切替手段（６２）とを備えることを特徴とする。
【００２０】
これにより、エジェクタサイクルにてホットガス運転モードを実現することができる。
【００２１】
請求項７に記載の発明では、室内熱交換器（３０）での熱負荷に基づいてノズル（４１）に流入する冷媒量を調節する流量調節手段（４６）を備えることを特徴とするものである。
【００２２】
請求項８に記載の発明では、冷媒として二酸化炭素が用いられていることを特徴とするものである。
【００２３】
請求項９に記載の発明では、高圧冷媒の圧力が、冷媒の臨界圧力以上となる超臨界運転モードを有することを特徴とするものである。
【００２４】
因みに、上記各手段の括弧内の符号は、後述する実施形態に記載の具体的手段との対応関係を示す一例である。
【００２５】
【発明の実施の形態】
（第１実施形態）
本実施形態は、本発明に係るエジェクタサイクルを車両用空調装置に適用したものであり、図１はエジェクタサイクルの模式図であり、図２は冷房運転時におけるエジェクタサイクルの全体のマクロ的作動を示すｐ−ｈ線図であり、図３は暖房運転（ホットガスモード）時におけるエジェクタサイクルの全体のマクロ的作動を示すｐ−ｈ線図である。
【００２６】
図１中、圧縮機１０は冷媒を吸入圧縮する圧縮機であり、本実施形態では、走行用エンジンから動力を得て稼動する連続可変容量型圧縮機を採用しているが、固定容量型の圧縮機を電動モータにて駆動してもよいことは言うまでもない。
【００２７】
なお、圧縮機１０から吐出される冷媒流量、つまり圧縮機１０の吐出容量は、後述する室内熱交換器３０で必要とされる能力、つまりクーラモード時にあっては必要冷凍能力、ホットガスモード時にあっては必要加熱能力となるように制御される。
【００２８】
室外熱交換器２０は圧縮機１０から吐出した冷媒と室外空気とを熱交換する熱交換器であり、室内熱交換器３０は室内に吹き出す空気と冷媒とを熱交換する熱交換器である。
【００２９】
ところで、本実施形態に係る室内熱交換器３０は、空気流れ上流側に配置された熱交換部と空気流れ下流側に配置された熱交換部とからなるもので、室内熱交換器３０内を流れる冷媒は、運転モードによらず、室内熱交換器３０を通過する空気の流れに対して、空気流れ下流側から空気流れ上流側に向かうように流れる。
【００３０】
エジェクタ４０は冷媒を減圧膨張させて、そのポンプ作用（ＪＩＳ Ｚ ８１２６ 番号２．１．２．３等参照）により室内熱交換器３０にて蒸発した気相冷媒を吸引しながら膨張エネルギーを圧力エネルギーに変換して圧縮機１０の吸入圧を上昇させるものである。
【００３１】
具体的には、エジェクタ４０は、流入する冷媒の圧力エネルギーを速度エネルギーに変換して冷媒を略等エントロピ的に減圧膨張させるノズル４１、ノズル４１から噴射する高い速度の冷媒流により室内熱交換器３０にて蒸発した気相冷媒を吸引しながら、ノズル４１から噴射する冷媒流とを混合する混合部４２、及びノズル４１から噴射する冷媒と室内熱交換器３０から吸引した冷媒とを混合させながら速度エネルギーを圧力エネルギーに変換して冷媒の圧力を昇圧させるディフューザ４３等からなるものである。
【００３２】
このとき、混合部４２においては、駆動流の運動量と吸引流の運動量との和が保存されるように駆動流と吸引流とが混合するので、混合部４２においても冷媒の圧力が（静圧）が上昇する。
【００３３】
一方、ディフューザ４３においては、通路断面積を徐々に拡大することにより、冷媒の速度エネルギ（動圧）を圧力エネルギ（静圧）に変換するので、エジェクタ４０においては、混合部４２及びディフューザ４３の両者にて冷媒圧力を昇圧する。そこで、混合部４２とディフューザ４３とを総称して昇圧部と呼ぶ。
【００３４】
因みに、本実施形態では、ノズル４１から噴出する冷媒の速度を音速以上まで加速するために、通路途中に通路面積が最も縮小した喉部を有するラバールノズル（流体工学（東京大学出版会）参照）を採用しているが、勿論、先細ノズルを採用してもよいことは言うまでもない。
【００３５】
また、気液分離器５０はエジェクタ４０から流出した冷媒が流入するとともに、その流入した冷媒を気相冷媒と液相冷媒とに分離して冷媒を蓄える気液分離手段であり、気液分離器５０の気相冷媒流出口は圧縮機１０の吸引側に接続され、液相冷媒流出口は室内熱交換器３０側の流入側に接続されている。
【００３６】
そして、気液分離器５０の液相冷媒流出口と室内熱交換器３０とを結ぶ冷媒通路は、冷媒が気液分離器５０側から室内熱交換器３０側にのみ流れることを許容し、液相冷媒流出口から気液分離器５０内に冷媒が逆流することを防止する逆止弁６１が設けられている。なお、本実施形態では、冷媒が気液分離器５０側から室内熱交換器３０側に流れるときに、逆止弁６１にて所定の圧力損失が発生するように設定されている。
【００３７】
因みに、本明細書に添付された図面中の逆止弁の記載は、ＪＩＳ Ｂ ０１２５（１９８８）に準拠したものである。
【００３８】
バイパス回路７０は圧縮機１０から吐出した冷媒をエジェクタ４０を迂回させて室内熱交換器３０に導く冷媒通路であり、減圧器７１はバイパス回路７０を経由して室内熱交換器３０に流れ込むホットガスを減圧する減圧手段であり、本実施形態では、この減圧器７１及びバイパス回路７０により特許請求の範囲に記載されたバイパス手段が構成されている。
【００３９】
そして、圧縮機１０の吐出側には、圧縮機１０から吐出する冷媒を室外熱交換器２０に供給するクーラモードと圧縮機１０から吐出する冷媒をバイパス回路７０に供給するホットガスモードとを切り替える切替手段をなす第１三方弁６２が設けられ、室内熱交換器３０の冷媒流出側には、室内熱交換器３０を流出した冷媒をエジェクタ４０の低圧冷媒吸引口４４に導くクーラモードと室内熱交換器３０を流出した冷媒をエジェクタ４０を迂回させて気液分離器５０に導くホットガスモードとを切り替える第２三方弁６３が設けられており、両三方弁６２、６３は、電子制御装置により制御されている。
【００４０】
次に、エジェクタサイクルの概略作動を述べる。
【００４１】
１．クーラモード（冷房運転）
図４に示すように、圧縮機１０から吐出した冷媒を室外熱交換器２０側に循環させる。これにより、室外熱交換器２０にて冷却された冷媒は、エジェクタ４０のノズル４１にて等エントロピ的に減圧膨張して、音速以上の速度で混合部４２内に流入する。
【００４２】
そして、混合部４２に流入した高速冷媒の巻き込み作用に伴うポンプ作用により、室内熱交換器３０にて室内に吹き出す空気から吸熱して蒸発した冷媒が混合部４２内に吸引されるため、低圧側の冷媒が気液分離器５０→室内熱交換器３０→エジェクタ４０（昇圧部）→気液分離器５０の順に循環する。
【００４３】
一方、室内熱交換器３０から吸引された冷媒（吸引流）とノズル４１から吹き出す冷媒（駆動流）とは、混合部４２にて混合しながらディフューザ４３にてその動圧が静圧に変換されて気液分離器５０に戻る。
【００４４】
なお、本実施形態では、冷媒を二酸化炭素とするとともに、室内熱交換器３０での熱負荷（冷房負荷）が大きいときには、図２に示すように、圧縮機１０にてノズル４１に流入する高圧の冷媒を冷媒の臨界圧力以上まで昇圧して必要な冷凍能力（冷房能力）を確保している。因みに、図２の●で示される符号は、図１に示す●で示される符号位置における冷媒の状態を示すものである。
【００４５】
２．ホットガスモード（暖房運転）
図５に示すように、圧縮機１０から吐出したホットガスをバイパス回路７０を介して室内熱交換器３０に導き、ホットガスにて室内に吹き出す空気を加熱する。
【００４６】
因みに、減圧器７１では、ホットガスを室内熱交換器３０の耐圧強度以下まで減圧することが目的であり、膨脹弁サイクルのごとく、気液二相状態まで冷媒を減圧するものではない。
【００４７】
なお、ホットガスモード時には、図３に示すように、圧縮機１０に吸入される冷媒の密度が小さくなるほど暖房能力が小さくなるので、減圧器７１で発生する圧力損失を除き、冷媒回路で発生する圧力損失はできるだけ小さいことは望ましい。
【００４８】
（第２実施形態）
第１実施形態では、第１、２三方弁６２、６３にて冷媒流れを切り換えたが、図６に示すように、二方弁６２ａ、６２ｂ、６３ａにて冷媒流れを切り換えるものである。
【００４９】
（第３実施形態）
上述の実施形態のホットガスモードでは、室内熱交換器３０を流出した冷媒をエジェクタ４０を迂回させて気液分離器５０に導いたが、図７に示すように、ホットガスモード時には、室内熱交換器３０を流出した冷媒をエジェクタ４０を経由させて気液分離器５０にに流入させるものである。
【００５０】
なお、図７では、室内熱交換器３０を流出した冷媒をエジェクタ４０の低圧冷媒吸引口４４及びノズル４１の冷媒入口４５に導いているが、本実施形態はこれに限定されものではなく、低圧冷媒吸引口４４及び冷媒入口４５のいずれか一方のみに室内熱交換器３０を流出した冷媒を導いてもよい。
【００５１】
（第４実施形態）
本実施形態は、冷媒入口４５の開度を流量調整手段をなす針状の弁体４６により調節することによりノズル４１に流入する高圧冷媒の流量及び圧力を可変制御するものである。
【００５２】
具体的には、図８に示すように、圧縮機１０の吐出側にエジェクタサイクル内を循環する冷媒の圧力を検出する圧力センサ８１を設け、室外熱交換器２０の冷媒流出口側に冷媒温度センサ８２を設けるとともに、これらセンサ８１、８２の検出信号を電子制御装置８０に入力する。
【００５３】
そして、電子制御装置８０は、圧力センサ８１の検出圧力、つまり高圧冷媒圧力が冷媒温度センサ８２の検出温度、つまり高圧冷媒温度によって決定される目標圧力となるようにアクチュエータ４７を介して弁体４６を稼動させる。
【００５４】
なお、冷媒流れの切り替えは、図８に示された弁６２、６３ａによる手法に限定されるものではないことは言うまでもない。
【００５５】
また、本実施形態では、室外熱交換器２０出口側の冷媒温度に基づいて冷媒入口４５の開度を制御したが、本実施形態はこれに限定されるものではなく、例えば室内熱交換器３０での空調負荷、又は室内熱交換器３０を流出した冷媒の過熱度に基づいて冷媒入口４５の開度を制御してもよい。
【００５６】
（第５実施形態）
上述の実施形態では、減圧器７１にて室内熱交換器３０に流入するホットガスを減圧したが、本実施形態は、図９、１０に示すように、エジェクタ４０を利用して室内熱交換器３０に流入するホットガスを減圧するものである。なお、三方弁６４は流体流れを切り換え制御するものである。
【００５７】
すなわち、図９に示す例では、ホットガスモード時に、圧縮機１０から吐出する冷媒を室外熱交換器２０を迂回させて、ノズル４１→室内熱交換器３０→気液分離器５０→前記圧縮機１０の順にホットガスを循環させることによりノズル４１でホットガスを循環させる。
【００５８】
また、図１０に示す例では、圧縮機１０から吐出する冷媒を室外熱交換器２０を迂回させてノズル４１の外壁部とハウジング部４８の内壁部との隙間に導き、室内熱交換器３０→気液分離器５０→圧縮機１０の順にホットガスを循環させることによりノズル４１の外壁部とハウジング部４８の内壁部との隙間でホットガスを循環させる。
【００５９】
なお、ハウジング部４８とは、ノズル４１を収納するとともに混合部４２の一部を構成するもので、本実施形態では、ハウジング部４８に低圧冷媒吸引口４４が設けられている。
【００６０】
（その他の実施形態）
上述の実施形態に係る室内熱交換器３０は、空気流れ上流側に配置された熱交換部と空気流れ下流側に配置された熱交換器とからなるものであったが、本発明に係る室内熱交換器３０はこれに限定されるものではない。
【００６１】
上述の実施形態では、車両用空調装置に本発明を適用したが、本発明はこれに限定されない。
【００６２】
上述の実施形態では、冷媒を二酸化炭素として高圧冷媒圧力を臨界圧力以上としたが、本発明はこれに限定されるものではない。
【図面の簡単な説明】
【図１】本発明の第１実施形態に係るエジェクタサイクルの模式図である。
【図２】冷房運転時におけるエジェクタサイクルの全体のマクロ的作動を示すｐ−ｈ線図である。
【図３】暖房運転（ホットガスモード）時におけるエジェクタサイクルの全体のマクロ的作動を示すｐ−ｈ線図である。
【図４】冷房運転時におけるエジェクタサイクルの冷媒流れを示す図である。
【図５】暖房運転時におけるエジェクタサイクルの冷媒流れを示す図である。
【図６】本発明の第２実施形態に係るエジェクタサイクルの模式図である。
【図７】本発明の第３実施形態に係るエジェクタサイクルの模式図である。
【図８】本発明の第４実施形態に係るエジェクタサイクルの模式図である。
【図９】本発明の第５実施形態に係るエジェクタサイクルの模式図である。
【図１０】本発明の第５実施形態に係るエジェクタサイクルの模式図である。
【符号の説明】
１０…圧縮機、２０…放熱器、３０…蒸発器、４０…エジェクタ、
５０…気液分離器、７０…バイパス回路、７１…減圧器。[0001]
BACKGROUND OF THE INVENTION
The present invention relates to an ejector cycle, and is effective when applied to a vehicle air conditioner.
[0002]
[Prior art]
The ejector cycle is a vapor compression refrigerator that sucks the gas-phase refrigerant that has been decompressed and expanded by the ejector and evaporated by the evaporator, and that increases the suction pressure of the compressor by converting the expansion energy into pressure energy. (For example, see Patent Document 1).
[0003]
On the other hand, as another type of vapor compression refrigerator, there is an expansion valve cycle in which high-pressure refrigerant is decompressed and supplied to an evaporator with a fixed throttle such as an orifice or a capillary tube, or a variable throttle such as a temperature type expansion valve. (For example, refer to Patent Document 2).
[0004]
[Patent Document 1]
JP-A-5-149652
[Patent Document 2]
US Pat. No. 6,178,761 specification
[Problems to be solved by the invention]
By the way, in the expansion valve cycle, the refrigerant becomes one refrigerant flow that circulates in the order of compressor → radiator → expansion valve → evaporator → compressor, whereas in the ejector cycle, the compressor → radiator → ejector → There is a refrigerant flow that circulates in the order of gas-liquid separator → compressor, and a refrigerant flow that circulates in the order of gas-liquid separator → evaporator → ejector → gas-liquid separator.
[0007]
For this reason, the heating operation cannot be performed by introducing the high-pressure / high-temperature refrigerant (hot gas) discharged from the compressor into the indoor heat exchanger in the same manner as the invention described in Patent Document 2.
[0008]
In view of the above, the present invention firstly provides a new ejector cycle different from the conventional one, and secondly, an object is to realize a hot gas operation mode in the ejector cycle.
[0009]
[Means for Solving the Problems]
In order to achieve the above object, the present invention provides an ejector cycle in which the low-pressure side refrigerant is evaporated to absorb heat from the low temperature side and dissipate heat to the high temperature side. Compressor (10), outdoor heat exchanger (20) for exchanging heat between the outdoor air and the refrigerant, indoor heat exchanger (30) for exchanging heat between the air blown into the room and the refrigerant, and decompressing the high-pressure refrigerant The compressor (10) has a nozzle (41) to be expanded, sucks the gas-phase refrigerant evaporated on the low pressure side by the high-speed refrigerant flow injected from the nozzle (41), and converts the expansion energy into pressure energy. An ejector (40) that raises the suction pressure of the gas, and the refrigerant that has flowed out of the ejector (40) is separated into a gas-phase refrigerant and a liquid-phase refrigerant, and the gas-phase refrigerant is supplied to the compressor (10). Gas-liquid separation supplied to the low pressure side (50), bypass means for bypassing the ejector (40) while depressurizing the refrigerant discharged from the compressor (10) and leading to the indoor heat exchanger (30), and the refrigerant discharged from the compressor (10) A first switching means (62) for switching between a cooler mode supplied to the heat exchanger (20) and a hot gas mode supplying refrigerant discharged from the compressor (10) to the bypass means; and in the cooler mode, an indoor heat exchanger The refrigerant flowing out from (30) is guided to the low-pressure refrigerant suction port of the ejector (40), and in the hot gas mode, the refrigerant flowing out from the indoor heat exchanger (30) is bypassed the ejector (40), and the gas-liquid separator And a second switching means (63) leading to (50) .
[0010]
Thereby, the hot gas operation mode can be realized in the ejector cycle.
[0011]
The invention according to claim 2 is an ejector cycle that evaporates the low-pressure side refrigerant, absorbs heat from the low-temperature side, and dissipates heat to the high-temperature side, and sucks and compresses the refrigerant, outdoor air, and refrigerant An outdoor heat exchanger (20) for exchanging heat with the air, an indoor heat exchanger (30) for exchanging heat between the air blown into the room and the refrigerant, and a nozzle (41) for decompressing and expanding the high-pressure refrigerant, 41) an ejector (40) for sucking the gas-phase refrigerant evaporated on the low-pressure side by a high-speed refrigerant flow injected from 41) and increasing the suction pressure of the compressor (10) by converting the expansion energy into pressure energy; A gas-liquid separator (50) that separates the refrigerant flowing out from the ejector (40) into a gas-phase refrigerant and a liquid-phase refrigerant, supplies the gas-phase refrigerant to the compressor (10), and supplies the liquid-phase refrigerant to the low pressure side. And discharged from the compressor (10) Bypass means for detouring the ejector (40) while depressurizing the refrigerant and guiding it to the indoor heat exchanger (30), and a cooler mode for supplying the refrigerant discharged from the compressor (10) to the outdoor heat exchanger (20) And a switching means (62) for switching between a hot gas mode for supplying the refrigerant discharged from the compressor (10) to the bypass means, and in the hot gas mode, the refrigerant flowing out of the indoor heat exchanger (30) is ejected (40 ).
[0012]
Thereby, the hot gas operation mode can be realized in the ejector cycle.
[0013]
The invention according to claim 3 is an ejector cycle that evaporates the refrigerant on the low pressure side, absorbs heat from the low temperature side, and dissipates heat to the high temperature side, and sucks and compresses the refrigerant, outdoor air, and refrigerant An outdoor heat exchanger (20) for exchanging heat with the air, an indoor heat exchanger (30) for exchanging heat between the air blown into the room and the refrigerant, and a nozzle (41) for decompressing and expanding the high-pressure refrigerant, 41) an ejector (40) for sucking the gas-phase refrigerant evaporated on the low-pressure side by a high-speed refrigerant flow injected from 41) and increasing the suction pressure of the compressor (10) by converting the expansion energy into pressure energy; A gas-liquid separator (50) that separates the refrigerant flowing out from the ejector (40) into a gas-phase refrigerant and a liquid-phase refrigerant, supplies the gas-phase refrigerant to the compressor (10), and supplies the liquid-phase refrigerant to the low pressure side. And discharged from the compressor (10) Bypass means for detouring the ejector (40) while depressurizing the refrigerant and guiding it to the indoor heat exchanger (30), and a cooler mode for supplying the refrigerant discharged from the compressor (10) to the outdoor heat exchanger (20) Switching means (62) for switching between a hot gas mode for supplying refrigerant discharged from the compressor (10) to the bypass means, and in the hot gas mode, the refrigerant flowing out of the indoor heat exchanger (30) 40) and the refrigerant inlet (45) of the nozzle (41).
[0014]
Thereby, the hot gas operation mode can be realized in the ejector cycle.
[0015]
In the invention according to claim 4, the refrigerant flowing in the indoor heat exchanger (30) flows in the air flowing through the indoor heat exchanger (30) in both cases of the cooler mode and the hot gas mode. On the other hand, it flows from the air flow downstream side toward the air flow upstream side.
[0016]
As a result, in the indoor heat exchanger (30), the refrigerant and air exchange heat in a counterflow or orthogonal counterflow state, so that the indoor heat exchanger (30) in both the cooler mode and the hot gas mode. The heat exchange efficiency in 30) can be kept high.
[0017]
The invention according to claim 5 is an ejector cycle that evaporates the low-pressure side refrigerant, absorbs heat from the low-temperature side, and dissipates heat to the high-temperature side, and sucks and compresses the refrigerant, outdoor air, and refrigerant An outdoor heat exchanger (20) for exchanging heat with the air, an indoor heat exchanger (30) for exchanging heat between the air blown into the room and the refrigerant, a nozzle (41) for decompressing and expanding the high-pressure refrigerant, and a nozzle (41) The velocity energy is converted into pressure energy by mixing the gas-phase refrigerant sucked while sucking the gas-phase refrigerant evaporated on the low-pressure side by the entrainment action of the refrigerant injected from the nozzle and the refrigerant injected from the nozzle (41). A pressure increasing section (42, 43) for increasing the pressure, an ejector (40) for increasing the suction pressure of the compressor (10), and a refrigerant flowing out of the ejector (40) into a gas phase refrigerant and a liquid phase refrigerant Min The gas-liquid separator (50) for supplying the gas-phase refrigerant to the compressor (10) and supplying the liquid-phase refrigerant to the low pressure side, and the refrigerant discharged from the compressor (10) as the outdoor heat exchanger (20). -> Nozzle (41)-> Booster (42, 43)-> Gas-liquid separator (50)-> Cooler mode that circulates in the order of the compressor (10) and refrigerant discharged from the compressor (10) in the outdoor heat exchanger (20 ), And switching means (62) for switching between the hot gas mode in which the nozzle (41), the indoor heat exchanger (30), the gas-liquid separator (50), and the compressor (10) are circulated in this order. It is characterized by that.
[0018]
Thereby, the hot gas operation mode can be realized in the ejector cycle.
[0019]
The invention according to claim 6 is an ejector cycle that evaporates the refrigerant on the low-pressure side, absorbs heat from the low-temperature side, and dissipates heat to the high-temperature side, and sucks and compresses the refrigerant, outdoor air, and refrigerant From the outdoor heat exchanger (20) for exchanging heat with the indoor heat exchanger (30) for exchanging heat between the air blown into the room and the refrigerant, the nozzle (41) and the nozzle (41) for decompressing and expanding the high-pressure refrigerant The refrigerant pressure is obtained by converting the velocity energy into pressure energy while mixing the gas-phase refrigerant sucked while sucking the gas-phase refrigerant evaporated on the low-pressure side by the entrainment action of the refrigerant to be injected and the refrigerant injected from the nozzle (41). And a housing part (48) for housing the nozzle (41) and constituting a part of the pressure raising part (42, 43), and the suction pressure of the compressor (10) Up The ejector (40) to be discharged, the refrigerant flowing out from the ejector (40) is separated into a gas phase refrigerant and a liquid phase refrigerant, the gas phase refrigerant is supplied to the compressor (10), and the liquid phase refrigerant is supplied to the low pressure side. The refrigerant discharged from the gas-liquid separator (50) and the compressor (10) is transferred to the outdoor heat exchanger (20) → the nozzle (41) → the booster (42, 43) → the gas-liquid separator (50) → the compressor. The cooler mode that circulates in the order of (10) and the refrigerant discharged from the compressor (10) bypasses the outdoor heat exchanger (20) and the gap between the outer wall portion of the nozzle (41) and the inner wall portion of the housing portion (48). And a switching means (62) for switching the hot gas mode to be circulated in the order of the indoor heat exchanger (30) → the gas-liquid separator (50) → the compressor (10).
[0020]
Thereby, the hot gas operation mode can be realized in the ejector cycle.
[0021]
The invention according to claim 7 is characterized by comprising flow rate adjusting means (46) for adjusting the amount of refrigerant flowing into the nozzle (41) based on the heat load in the indoor heat exchanger (30). is there.
[0022]
The invention according to claim 8 is characterized in that carbon dioxide is used as the refrigerant.
[0023]
The invention described in claim 9 has a supercritical operation mode in which the pressure of the high-pressure refrigerant is equal to or higher than the critical pressure of the refrigerant.
[0024]
Factor mini, reference numerals in parentheses of the above means are examples showing the correspondence with specific means described in embodiments described later.
[0025]
DETAILED DESCRIPTION OF THE INVENTION
(First embodiment)
This embodiment, the ejector cycle according to the present invention are those applied to the vehicle air-conditioning system, FIG. 1 is a schematic diagram of the ejector cycle, the macroscopic overall operation of the ejector cycle at 2 cooling operation FIG. 3 is a ph diagram showing an overall macro operation of the ejector cycle during heating operation (hot gas mode).
[0026]
In FIG. 1, a compressor 10 is a compressor that sucks and compresses refrigerant. In this embodiment, a continuously variable capacity compressor that operates by obtaining power from a traveling engine is employed. Needless to say, the compressor may be driven by an electric motor.
[0027]
Note that the flow rate of refrigerant discharged from the compressor 10, that is, the discharge capacity of the compressor 10, is the capacity required by the indoor heat exchanger 30 described later, that is, the required refrigeration capacity in the cooler mode, and the hot gas mode. In that case, it is controlled so as to achieve the required heating capacity.
[0028]
The outdoor heat exchanger 20 is a heat exchanger that exchanges heat between the refrigerant discharged from the compressor 10 and outdoor air, and the indoor heat exchanger 30 is a heat exchanger that exchanges heat between the air blown into the room and the refrigerant.
[0029]
By the way, the indoor heat exchanger 30 according to the present embodiment is composed of a heat exchanging part arranged on the upstream side of the air flow and a heat exchanging part arranged on the downstream side of the air flow. Regardless of the operation mode, the flowing refrigerant flows from the air flow downstream side toward the air flow upstream side with respect to the air flow passing through the indoor heat exchanger 30.
[0030]
The ejector 40 expands the refrigerant under reduced pressure and converts the expansion energy into pressure energy while sucking the gas-phase refrigerant evaporated in the indoor heat exchanger 30 by its pumping action (see JIS Z 8126 number 2.1.2.3). To increase the suction pressure of the compressor 10.
[0031]
Specifically, the ejector 40 converts the pressure energy of the refrigerant flowing into the velocity energy, the nozzle 41 that decompresses and expands the refrigerant in a substantially isentropic manner, and the indoor heat exchanger using a high-speed refrigerant flow that is ejected from the nozzle 41. While mixing the gas-phase refrigerant evaporated at 30, the mixing unit 42 that mixes the refrigerant flow injected from the nozzle 41, and the refrigerant injected from the nozzle 41 and the refrigerant sucked from the indoor heat exchanger 30 are mixed It comprises a diffuser 43 or the like that converts velocity energy into pressure energy to increase the pressure of the refrigerant.
[0032]
At this time, in the mixing unit 42, the driving flow and the suction flow are mixed so that the sum of the momentum of the driving flow and the momentum of the suction flow is preserved. ) Will rise.
[0033]
On the other hand, in the diffuser 43, the velocity energy (dynamic pressure) of the refrigerant is converted into pressure energy (static pressure) by gradually increasing the cross-sectional area of the passage, so that in the ejector 40, the mixing section 42 and the diffuser 43 Both increase the refrigerant pressure. Therefore, the mixing unit 42 and the diffuser 43 are collectively referred to as a boosting unit.
[0034]
By the way, in this embodiment, in order to accelerate the speed of the refrigerant ejected from the nozzle 41 to the speed of sound or more, a Laval nozzle (see Fluid Engineering (Tokyo University Press)) having a throat with the smallest passage area in the middle of the passage is provided. Needless to say, a tapered nozzle may be adopted as a matter of course.
[0035]
The gas-liquid separator 50 is a gas-liquid separator that stores the refrigerant by flowing the refrigerant flowing out from the ejector 40 into the vapor-phase refrigerant and the liquid-phase refrigerant. The gas-phase refrigerant outlet 50 is connected to the suction side of the compressor 10, and the liquid-phase refrigerant outlet is connected to the inflow side on the indoor heat exchanger 30 side.
[0036]
The refrigerant passage connecting the liquid-phase refrigerant outlet of the gas-liquid separator 50 and the indoor heat exchanger 30 allows the refrigerant to flow only from the gas-liquid separator 50 side to the indoor heat exchanger 30 side, A check valve 61 is provided to prevent the refrigerant from flowing back into the gas-liquid separator 50 from the phase refrigerant outlet. In the present embodiment, the check valve 61 is set to generate a predetermined pressure loss when the refrigerant flows from the gas-liquid separator 50 side to the indoor heat exchanger 30 side.
[0037]
Incidentally, the description of the check valve in the drawings attached to the present specification is based on JIS B 0125 (1988).
[0038]
The bypass circuit 70 is a refrigerant passage that guides the refrigerant discharged from the compressor 10 to the indoor heat exchanger 30 by bypassing the ejector 40, and the decompressor 71 is hot gas that flows into the indoor heat exchanger 30 via the bypass circuit 70. In this embodiment, the decompressor 71 and the bypass circuit 70 constitute bypass means described in the claims.
[0039]
On the discharge side of the compressor 10, a cooler mode for supplying the refrigerant discharged from the compressor 10 to the outdoor heat exchanger 20 and a hot gas mode for supplying the refrigerant discharged from the compressor 10 to the bypass circuit 70 are switched. A first three-way valve 62 serving as a switching unit is provided, and on the refrigerant outflow side of the indoor heat exchanger 30, a cooler mode that guides the refrigerant that has flowed out of the indoor heat exchanger 30 to the low-pressure refrigerant suction port 44 of the ejector 40, and indoor heat A second three-way valve 63 is provided for switching between a hot gas mode in which the refrigerant flowing out of the exchanger 30 bypasses the ejector 40 and is led to the gas-liquid separator 50. Both the three-way valves 62 and 63 are controlled by an electronic control unit. It is controlled.
[0040]
Next, the general operation of the ejector cycle will be described.
[0041]
1. Cooler mode (cooling operation)
As shown in FIG. 4, the refrigerant discharged from the compressor 10 is circulated to the outdoor heat exchanger 20 side. Thereby, the refrigerant cooled in the outdoor heat exchanger 20 is isentropically decompressed and expanded at the nozzle 41 of the ejector 40 and flows into the mixing unit 42 at a speed higher than the speed of sound.
[0042]
Since the refrigerant that has absorbed heat from the air blown into the room in the indoor heat exchanger 30 is sucked into the mixing part 42 by the pump action accompanying the entrainment action of the high-speed refrigerant flowing into the mixing part 42, the low pressure side The refrigerant circulates in the order of the gas-liquid separator 50 → the indoor heat exchanger 30 → the ejector 40 (pressure increase unit) → the gas-liquid separator 50.
[0043]
On the other hand, the refrigerant sucked from the indoor heat exchanger 30 (suction flow) and the refrigerant blown from the nozzle 41 (driving flow) are mixed by the mixing unit 42 and the dynamic pressure thereof is converted to static pressure by the diffuser 43. Return to the gas-liquid separator 50.
[0044]
In the present embodiment, when the refrigerant is carbon dioxide and the heat load (cooling load) in the indoor heat exchanger 30 is large, the high pressure flowing into the nozzle 41 by the compressor 10 as shown in FIG. The required refrigerant capacity (cooling capacity) is ensured by increasing the pressure of the refrigerant to above the critical pressure of the refrigerant. Incidentally, the symbol indicated by ● in FIG. 2 indicates the state of the refrigerant at the symbol position indicated by ● in FIG.
[0045]
2. Hot gas mode (heating operation)
As shown in FIG. 5, the hot gas discharged from the compressor 10 is led to the indoor heat exchanger 30 through the bypass circuit 70, and the air blown into the room is heated with the hot gas.
[0046]
Incidentally, the purpose of the decompressor 71 is to depressurize the hot gas to the pressure strength or less of the indoor heat exchanger 30 and does not decompress the refrigerant to the gas-liquid two-phase state as in the expansion valve cycle.
[0047]
In the hot gas mode, as shown in FIG. 3, the heating capacity decreases as the density of the refrigerant sucked into the compressor 10 decreases. Therefore, the pressure is generated in the refrigerant circuit except for the pressure loss generated in the decompressor 71. It is desirable that the pressure loss be as small as possible.
[0048]
(Second Embodiment)
In the first embodiment, the refrigerant flow is switched by the first and second three-way valves 62 and 63. However, as shown in FIG. 6, the refrigerant flow is switched by the two-way valves 62a, 62b and 63a.
[0049]
(Third embodiment)
In the hot gas mode of the above-described embodiment, the refrigerant that has flowed out of the indoor heat exchanger 30 is guided to the gas-liquid separator 50 by bypassing the ejector 40. However, as shown in FIG. The refrigerant that has flowed out of the exchanger 30 is caused to flow into the gas-liquid separator 50 via the ejector 40.
[0050]
In FIG. 7, the refrigerant that has flowed out of the indoor heat exchanger 30 is led to the low-pressure refrigerant suction port 44 of the ejector 40 and the refrigerant inlet 45 of the nozzle 41, but this embodiment is not limited to this, The refrigerant that has flowed out of the indoor heat exchanger 30 may be guided to only one of the refrigerant suction port 44 and the refrigerant inlet 45.
[0051]
(Fourth embodiment)
In the present embodiment, the flow rate and pressure of the high-pressure refrigerant flowing into the nozzle 41 are variably controlled by adjusting the opening degree of the refrigerant inlet 45 with a needle-like valve body 46 serving as a flow rate adjusting means.
[0052]
Specifically, as shown in FIG. 8, a pressure sensor 81 for detecting the pressure of the refrigerant circulating in the ejector cycle is provided on the discharge side of the compressor 10, and the refrigerant temperature is provided on the refrigerant outlet side of the outdoor heat exchanger 20. A sensor 82 is provided, and detection signals from these sensors 81 and 82 are input to the electronic control unit 80.
[0053]
The electronic control unit 80 then connects the valve body 46 via the actuator 47 so that the detected pressure of the pressure sensor 81, that is, the high-pressure refrigerant pressure becomes the target pressure determined by the detected temperature of the refrigerant temperature sensor 82, that is, the high-pressure refrigerant temperature. Activate.
[0054]
Needless to say, the switching of the refrigerant flow is not limited to the method using the valves 62 and 63a shown in FIG.
[0055]
Moreover, in this embodiment, although the opening degree of the refrigerant | coolant inlet 45 was controlled based on the refrigerant | coolant temperature of the outdoor heat exchanger 20 exit side, this embodiment is not limited to this, For example, the indoor heat exchanger 30 The opening degree of the refrigerant inlet 45 may be controlled on the basis of the air conditioning load or the degree of superheat of the refrigerant flowing out of the indoor heat exchanger 30.
[0056]
(Fifth embodiment)
In the above-described embodiment, the hot gas flowing into the indoor heat exchanger 30 is decompressed by the decompressor 71. However, in this embodiment, as shown in FIGS. The hot gas flowing into 30 is decompressed. The three-way valve 64 switches and controls the fluid flow.
[0057]
That is, in the example shown in FIG. 9, in the hot gas mode, the refrigerant discharged from the compressor 10 bypasses the outdoor heat exchanger 20, and the nozzle 41 → the indoor heat exchanger 30 → the gas-liquid separator 50 → the compressor The hot gas is circulated by the nozzle 41 by circulating the hot gas in the order of 10.
[0058]
Further, in the example shown in FIG. 10, the refrigerant discharged from the compressor 10 is guided to the gap between the outer wall portion of the nozzle 41 and the inner wall portion of the housing portion 48 by bypassing the outdoor heat exchanger 20, and the indoor heat exchanger 30 → Hot gas is circulated in the gap between the outer wall portion of the nozzle 41 and the inner wall portion of the housing portion 48 by circulating the hot gas in the order of the gas-liquid separator 50 → the compressor 10.
[0059]
The housing part 48 houses the nozzle 41 and constitutes a part of the mixing part 42. In the present embodiment, the housing part 48 is provided with a low-pressure refrigerant suction port 44.
[0060]
(Other embodiments)
The indoor heat exchanger 30 according to the above-described embodiment is composed of the heat exchange unit disposed on the upstream side of the air flow and the heat exchanger disposed on the downstream side of the air flow. The heat exchanger 30 is not limited to this.
[0061]
In the above embodiment, the invention is applied to a vehicle air conditioner, the present invention is Lena have limited thereto.
[0062]
In the above embodiment, the refrigerant is carbon dioxide and the high-pressure refrigerant pressure is set to be equal to or higher than the critical pressure, but the present invention is not limited to this.
[Brief description of the drawings]
FIG. 1 is a schematic diagram of an ejector cycle according to a first embodiment of the present invention.
FIG. 2 is a ph diagram showing an overall macro operation of an ejector cycle during cooling operation.
FIG. 3 is a ph diagram showing an overall macro operation of the ejector cycle during heating operation (hot gas mode).
FIG. 4 is a diagram showing a refrigerant flow in an ejector cycle during cooling operation.
FIG. 5 is a diagram showing a refrigerant flow in an ejector cycle during heating operation.
FIG. 6 is a schematic diagram of an ejector cycle according to a second embodiment of the present invention.
FIG. 7 is a schematic diagram of an ejector cycle according to a third embodiment of the present invention.
FIG. 8 is a schematic diagram of an ejector cycle according to a fourth embodiment of the present invention.
FIG. 9 is a schematic diagram of an ejector cycle according to a fifth embodiment of the present invention.
FIG. 10 is a schematic diagram of an ejector cycle according to a fifth embodiment of the present invention.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 10 ... Compressor, 20 ... Radiator, 30 ... Evaporator, 40 ... Ejector,
50: Gas-liquid separator, 70: Bypass circuit, 71: Pressure reducer.

Claims (9)

低圧側の冷媒を蒸発させて低温側から吸熱し、高温側に放熱するエジェクタサイクルであって、
冷媒を吸入圧縮する圧縮機（１０）と、
室外空気と冷媒とを熱交換する室外熱交換器（２０）と、
室内に吹き出す空気と冷媒とを熱交換する室内熱交換器（３０）と、
高圧冷媒を減圧膨張させるノズル（４１）を有し、前記ノズル（４１）から噴射する高い速度の冷媒流により低圧側で蒸発した気相冷媒を吸引するとともに、膨張エネルギーを圧力エネルギーに変換して前記圧縮機（１０）の吸入圧を上昇させるエジェクタ（４０）と、
前記エジェクタ（４０）から流出した冷媒を気相冷媒と液相冷媒とに分離し、気相冷媒を前記圧縮機（１０）に供給し、液相冷媒を低圧側に供給する気液分離器（５０）と、
前記圧縮機（１０）から吐出した冷媒を減圧させながら前記エジェクタ（４０）を迂回させて前記室内熱交換器（３０）に導くバイパス手段と、
前記圧縮機（１０）から吐出する冷媒を前記室外熱交換器（２０）に供給するクーラモードと前記圧縮機（１０）から吐出する冷媒を前記バイパス手段に供給するホットガスモードとを切り替える第１切替手段（６２）と、
前記クーラモード時には、前記室内熱交換器（３０）から流出した冷媒を前記エジェクタ（４０）の低圧冷媒吸引口に導き、前記ホットガスモード時には、前記室内熱交換器（３０）から流出した冷媒を前記エジェクタ（４０）を迂回させて、前記気液分離器（５０）に導く第２切替手段（６３）とを備えることを特徴とするエジェクタサイクル。Ejector cycle that evaporates the low-pressure side refrigerant, absorbs heat from the low temperature side, and dissipates heat to the high temperature side,
A compressor (10) for sucking and compressing refrigerant;
An outdoor heat exchanger (20) for exchanging heat between the outdoor air and the refrigerant;
An indoor heat exchanger (30) for exchanging heat between the air blown into the room and the refrigerant;
It has a nozzle (41) that decompresses and expands the high-pressure refrigerant, sucks the gas-phase refrigerant evaporated on the low-pressure side by the high-speed refrigerant flow injected from the nozzle (41), and converts the expansion energy into pressure energy. An ejector (40) for increasing the suction pressure of the compressor (10);
A gas-liquid separator that separates the refrigerant flowing out of the ejector (40) into a gas-phase refrigerant and a liquid-phase refrigerant, supplies the gas-phase refrigerant to the compressor (10), and supplies the liquid-phase refrigerant to the low-pressure side ( 50),
Bypass means for bypassing the ejector (40) and reducing the refrigerant discharged from the compressor (10) to the indoor heat exchanger (30);
A first mode is switched between a cooler mode for supplying refrigerant discharged from the compressor (10) to the outdoor heat exchanger (20) and a hot gas mode for supplying refrigerant discharged from the compressor (10) to the bypass means. Switching means (62);
In the cooler mode, the refrigerant flowing out of the indoor heat exchanger (30) is guided to the low-pressure refrigerant suction port of the ejector (40), and in the hot gas mode, the refrigerant flowing out of the indoor heat exchanger (30) is discharged. An ejector cycle, comprising: a second switching means (63) that bypasses the ejector (40) and leads to the gas-liquid separator (50). 低圧側の冷媒を蒸発させて低温側から吸熱し、高温側に放熱するエジェクタサイクルであって、
冷媒を吸入圧縮する圧縮機（１０）と、
室外空気と冷媒とを熱交換する室外熱交換器（２０）と、
室内に吹き出す空気と冷媒とを熱交換する室内熱交換器（３０）と、
高圧冷媒を減圧膨張させるノズル（４１）を有し、前記ノズル（４１）から噴射する高い速度の冷媒流により低圧側で蒸発した気相冷媒を吸引するとともに、膨張エネルギーを圧力エネルギーに変換して前記圧縮機（１０）の吸入圧を上昇させるエジェクタ（４０）と、
前記エジェクタ（４０）から流出した冷媒を気相冷媒と液相冷媒とに分離し、気相冷媒を前記圧縮機（１０）に供給し、液相冷媒を低圧側に供給する気液分離器（５０）と、
前記圧縮機（１０）から吐出した冷媒を減圧させながら前記エジェクタ（４０）を迂回させて前記室内熱交換器（３０）に導くバイパス手段と、
前記圧縮機（１０）から吐出する冷媒を前記室外熱交換器（２０）に供給するクーラモードと前記圧縮機（１０）から吐出する冷媒を前記バイパス手段に供給するホットガスモードとを切り替える切替手段（６２）とを備え、
前記ホットガスモード時には、前記室内熱交換器（３０）を流出した冷媒を前記エジェクタ（４０）に流入させることを備えることを特徴とするエジェクタサイクル。Ejector cycle that evaporates the low-pressure side refrigerant, absorbs heat from the low temperature side, and dissipates heat to the high temperature side,
A compressor (10) for sucking and compressing refrigerant;
An outdoor heat exchanger (20) for exchanging heat between the outdoor air and the refrigerant;
An indoor heat exchanger (30) for exchanging heat between the air blown into the room and the refrigerant;
It has a nozzle (41) that decompresses and expands the high-pressure refrigerant, sucks the gas-phase refrigerant evaporated on the low-pressure side by the high-speed refrigerant flow injected from the nozzle (41), and converts the expansion energy into pressure energy. An ejector (40) for increasing the suction pressure of the compressor (10);
A gas-liquid separator that separates the refrigerant flowing out of the ejector (40) into a gas-phase refrigerant and a liquid-phase refrigerant, supplies the gas-phase refrigerant to the compressor (10), and supplies the liquid-phase refrigerant to the low-pressure side ( 50),
Bypass means for bypassing the ejector (40) and reducing the refrigerant discharged from the compressor (10) to the indoor heat exchanger (30);
Switching means for switching between a cooler mode for supplying refrigerant discharged from the compressor (10) to the outdoor heat exchanger (20) and a hot gas mode for supplying refrigerant discharged from the compressor (10) to the bypass means. (62)
In the hot gas mode, the ejector cycle comprising flowing the refrigerant that has flowed out of the indoor heat exchanger (30) into the ejector (40). 低圧側の冷媒を蒸発させて低温側から吸熱し、高温側に放熱するエジェクタサイクルであって、
冷媒を吸入圧縮する圧縮機（１０）と、
室外空気と冷媒とを熱交換する室外熱交換器（２０）と、
室内に吹き出す空気と冷媒とを熱交換する室内熱交換器（３０）と、
高圧冷媒を減圧膨張させるノズル（４１）を有し、前記ノズル（４１）から噴射する高い速度の冷媒流により低圧側で蒸発した気相冷媒を吸引するとともに、膨張エネルギーを圧力エネルギーに変換して前記圧縮機（１０）の吸入圧を上昇させるエジェクタ（４０）と、
前記エジェクタ（４０）から流出した冷媒を気相冷媒と液相冷媒とに分離し、気相冷媒を前記圧縮機（１０）に供給し、液相冷媒を低圧側に供給する気液分離器（５０）と、
前記圧縮機（１０）から吐出した冷媒を減圧させながら前記エジェクタ（４０）を迂回させて前記室内熱交換器（３０）に導くバイパス手段と、
前記圧縮機（１０）から吐出する冷媒を前記室外熱交換器（２０）に供給するクーラモードと前記圧縮機（１０）から吐出する冷媒を前記バイパス手段に供給するホットガスモードとを切り替える切替手段（６２）とを備え、
前記ホットガスモード時には、前記室内熱交換器（３０）を流出した冷媒を、前記エジェクタ（４０）の低圧冷媒吸引口（４４）及び前記ノズル（４１）の冷媒入口（４５）に導くことを特徴とするエジェクタサイクル。Ejector cycle that evaporates the low-pressure side refrigerant, absorbs heat from the low temperature side, and dissipates heat to the high temperature side,
A compressor (10) for sucking and compressing refrigerant;
An outdoor heat exchanger (20) for exchanging heat between the outdoor air and the refrigerant;
An indoor heat exchanger (30) for exchanging heat between the air blown into the room and the refrigerant;
It has a nozzle (41) that decompresses and expands the high-pressure refrigerant, sucks the gas-phase refrigerant evaporated on the low-pressure side by the high-speed refrigerant flow injected from the nozzle (41), and converts the expansion energy into pressure energy. An ejector (40) for increasing the suction pressure of the compressor (10);
A gas-liquid separator that separates the refrigerant flowing out of the ejector (40) into a gas-phase refrigerant and a liquid-phase refrigerant, supplies the gas-phase refrigerant to the compressor (10), and supplies the liquid-phase refrigerant to the low-pressure side ( 50),
Bypass means for bypassing the ejector (40) and reducing the refrigerant discharged from the compressor (10) to the indoor heat exchanger (30);
Switching means for switching between a cooler mode for supplying refrigerant discharged from the compressor (10) to the outdoor heat exchanger (20) and a hot gas mode for supplying refrigerant discharged from the compressor (10) to the bypass means. (62)
In the hot gas mode, the refrigerant flowing out of the indoor heat exchanger (30) is guided to the low-pressure refrigerant suction port (44) of the ejector (40) and the refrigerant inlet (45) of the nozzle (41). Ejector cycle. 前記クーラモード時及び前記ホットガスモード時のいずれの場合においても、前記室内熱交換器（３０）内を流れる冷媒は、前記室内熱交換器（３０）を通過する空気の流れに対して、空気流れ下流側から空気流れ上流側に向かうように流れることを特徴とする請求項１ないし３のいずれか１つに記載のエジェクタサイクル。  In both cases of the cooler mode and the hot gas mode, the refrigerant flowing in the indoor heat exchanger (30) is in the air flow relative to the air flow passing through the indoor heat exchanger (30). The ejector cycle according to any one of claims 1 to 3, wherein the ejector cycle flows from the downstream side to the upstream side of the air flow. 低圧側の冷媒を蒸発させて低温側から吸熱し、高温側に放熱するエジェクタサイクルであって、
冷媒を吸入圧縮する圧縮機（１０）と、
室外空気と冷媒とを熱交換する室外熱交換器（２０）と、
室内に吹き出す空気と冷媒とを熱交換する室内熱交換器（３０）と、
高圧冷媒を減圧膨張させるノズル（４１）、及び前記ノズル（４１）から噴射する冷媒の巻き込み作用により低圧側で蒸発した気相冷媒を吸引しながら吸引した気相冷媒と前記ノズル（４１）から噴射する冷媒とを混合させながら速度エネルギーを圧力エネルギーに変換して冷媒の圧力を昇圧させる昇圧部（４２、４３）を有し、前記圧縮機（１０）の吸入圧を上昇させるエジェクタ（４０）と、
前記エジェクタ（４０）から流出した冷媒を気相冷媒と液相冷媒とに分離し、気相冷媒を前記圧縮機（１０）に供給し、液相冷媒を低圧側に供給する気液分離器（５０）と、
前記圧縮機（１０）から吐出する冷媒を前記室外熱交換器（２０）→前記ノズル（４１）→前記昇圧部（４２、４３）→前記気液分離器（５０）→前記圧縮機（１０）の順に循環させるクーラモードと前記圧縮機（１０）から吐出する冷媒を前記室外熱交換器（２０）を迂回させて、前記ノズル（４１）→前記室内熱交換器（３０）→前記気液分離器（５０）→前記圧縮機（１０）の順に循環させるホットガスモードとを切り替える切替手段（６２）とを備えることを特徴とするエジェクタサイクル。Ejector cycle that evaporates the low-pressure side refrigerant, absorbs heat from the low temperature side, and dissipates heat to the high temperature side,
A compressor (10) for sucking and compressing refrigerant;
An outdoor heat exchanger (20) for exchanging heat between the outdoor air and the refrigerant;
An indoor heat exchanger (30) for exchanging heat between the air blown into the room and the refrigerant;
A nozzle (41) that decompresses and expands the high-pressure refrigerant, and a gas-phase refrigerant sucked while sucking the gas-phase refrigerant evaporated on the low-pressure side by the entrainment action of the refrigerant injected from the nozzle (41) and the nozzle (41) An ejector (40) for increasing the suction pressure of the compressor (10), having a boosting section (42, 43) for increasing the pressure of the refrigerant by converting velocity energy into pressure energy while mixing with the refrigerant ,
A gas-liquid separator that separates the refrigerant flowing out of the ejector (40) into a gas-phase refrigerant and a liquid-phase refrigerant, supplies the gas-phase refrigerant to the compressor (10), and supplies the liquid-phase refrigerant to the low-pressure side ( 50),
The refrigerant discharged from the compressor (10) is the outdoor heat exchanger (20) → the nozzle (41) → the booster (42, 43) → the gas-liquid separator (50) → the compressor (10). In this order, the cooler mode is circulated and the refrigerant discharged from the compressor (10) bypasses the outdoor heat exchanger (20), and the nozzle (41) → the indoor heat exchanger (30) → the gas-liquid separation. An ejector cycle comprising switching means (62) for switching between a hot gas mode for circulating in the order of the compressor (50) → the compressor (10). 低圧側の冷媒を蒸発させて低温側から吸熱し、高温側に放熱するエジェクタサイクルであって、
冷媒を吸入圧縮する圧縮機（１０）と、
室外空気と冷媒とを熱交換する室外熱交換器（２０）と、
室内に吹き出す空気と冷媒とを熱交換する室内熱交換器（３０）と、
高圧冷媒を減圧膨張させるノズル（４１）、前記ノズル（４１）から噴射する冷媒の巻き込み作用により低圧側で蒸発した気相冷媒を吸引しながら吸引した気相冷媒と前記ノズル（４１）から噴射する冷媒とを混合させながら速度エネルギーを圧力エネルギーに変換して冷媒の圧力を昇圧させる昇圧部（４２、４３）、及び前記ノズル（４１）を収納するとともに前記昇圧部（４２、４３）の一部を構成するハウジング部（４８）を有し、前記圧縮機（１０）の吸入圧を上昇させるエジェクタ（４０）と、
前記エジェクタ（４０）から流出した冷媒を気相冷媒と液相冷媒とに分離し、気相冷媒を前記圧縮機（１０）に供給し、液相冷媒を低圧側に供給する気液分離器（５０）と、
前記圧縮機（１０）から吐出する冷媒を前記室外熱交換器（２０）→前記ノズル（４１）→前記昇圧部（４２、４３）→前記気液分離器（５０）→前記圧縮機（１０）の順に循環させるクーラモードと前記圧縮機（１０）から吐出する冷媒を前記室外熱交換器（２０）を迂回させて前記ノズル（４１）の外壁部と前記ハウジング部（４８）の内壁部との隙間に導き、前記室内熱交換器（３０）→前記気液分離器（５０）→前記圧縮機（１０）の順に循環させるホットガスモードとを切り替える切替手段（６２）とを備えることを特徴とするエジェクタサイクル。Ejector cycle that evaporates the low-pressure side refrigerant, absorbs heat from the low temperature side, and dissipates heat to the high temperature side,
A compressor (10) for sucking and compressing refrigerant;
An outdoor heat exchanger (20) for exchanging heat between the outdoor air and the refrigerant;
An indoor heat exchanger (30) for exchanging heat between the air blown into the room and the refrigerant;
A nozzle (41) that decompresses and expands the high-pressure refrigerant, and injects the gas-phase refrigerant sucked while sucking the gas-phase refrigerant evaporated on the low-pressure side by the entrainment action of the refrigerant injected from the nozzle (41) and the nozzle (41). A pressure-increasing part (42, 43) for increasing the pressure of the refrigerant by converting velocity energy to pressure energy while mixing with the refrigerant, and a part of the pressure-increasing part (42, 43) while accommodating the nozzle (41) An ejector (40) having a housing part (48) constituting the compressor and increasing the suction pressure of the compressor (10),
A gas-liquid separator that separates the refrigerant flowing out of the ejector (40) into a gas-phase refrigerant and a liquid-phase refrigerant, supplies the gas-phase refrigerant to the compressor (10), and supplies the liquid-phase refrigerant to the low-pressure side ( 50),
The refrigerant discharged from the compressor (10) is the outdoor heat exchanger (20) → the nozzle (41) → the booster (42, 43) → the gas-liquid separator (50) → the compressor (10). Between the outer wall part of the nozzle (41) and the inner wall part of the housing part (48) by bypassing the outdoor heat exchanger (20) with the cooler mode circulated in this order and the refrigerant discharged from the compressor (10). And a switching means (62) for switching the hot gas mode to be circulated in the order of the indoor heat exchanger (30) → the gas-liquid separator (50) → the compressor (10). Ejector cycle. 前記室内熱交換器（３０）での熱負荷に基づいて前記ノズル（４１）に流入する冷媒量を調節する流量調節手段（４６）を備えることを特徴とする請求項１ないし６に記載のエジェクタサイクル。  The ejector according to any one of claims 1 to 6, further comprising a flow rate adjusting means (46) for adjusting a refrigerant amount flowing into the nozzle (41) based on a heat load in the indoor heat exchanger (30). cycle. 冷媒として二酸化炭素が用いられていることを特徴とする請求項１ないし７に記載のエジェクタサイクル。  8. The ejector cycle according to claim 1, wherein carbon dioxide is used as the refrigerant. 高圧冷媒の圧力が、冷媒の臨界圧力以上となる超臨界運転モードを有することを特徴とする請求項１ないし８に記載のエジェクタサイクル。  The ejector cycle according to claim 1, wherein the high-pressure refrigerant has a supercritical operation mode in which the pressure of the high-pressure refrigerant is equal to or higher than the critical pressure of the refrigerant.
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